Power transmission



Allg 15, 1938- oxE. FlsHBURN Er A1.. 2,127,354

POWER TRANSMISSION I.Original Filed Dec. 1'7, 1934 4 Sheets--Shee't 1 BIO A TTORNEYS.

Aug. 16, 1938. o. E. FlsHBuRN Er A1. 2,127,354

POWER TRANSMISSION Original Filed Dec. 17, 1934 4 Sheets-Sheet 2 /llll/ll/lll O"lill/111111111111111 4 Aug. 16; 1938. o. E'. FlsHBURN ET AL 2,127,354

POWER TRANSMISSION OriginalAFiled Dec. 17, 1934 4 Sheets-Sheet 3 o. E. FISHBURN Er Al. 2,127,354

POWER TRANSMISSION Original FriledDec. 17, 1934 4 Sheets-Sheet 4 Aug. 16, 193s.

Patented Aug. 16, 193s UNITED STATES PATENT oFElcE POWER TRANSMISSION vOriginal application December 17, 1934, Serial No. 757,748. Divided and this application January 19, 1935, Serial No. 2,500 i 22 Claims.

This invention relates to driving mechanisms and refers more particularly, in one embodiment thereof, to improvementsy in driving mechanisms .for motor cars or vehicles, especially where it is desired to vary the driving speed ratio between the vehicle engine or prime mover and the propelling ground wheels..

One object of our invention resides in the provision of an improved driving mechanism adapted, under predetermined desired conditions, to automatically eiect the drive for the vehicle. Our driving mechanism is preferably adapted for use in connection with a speed ratio changing transmission and is adapted to establish an auxiliary driving speed ratio for the vehicle,'such as an overdrive ratio, for example.

A further object oi our invention resides in the provision of an improved driving or speed ratio changing transmission adapted to automatically respond in its'actuation to predetermined desired conditions of operation of the vehicle. Thus, by way of example, We have provided an overdrive which is automatically effective in an improved manner when the vehicle attains a predetermined speed so that, on reaching this critical speed, the overdrive becomes effective and on falling below this critical speed, the overdrive becomes ineffective.

Another object of our invention is to improve and simplify the cooling of the gear driving mechanism employed in our overdriving mechanism. Thus, we have provided a lubricating oil reservoir with means for circulating the oil between the reservoir and overdrive mechanism. More particularly, we preferably utilize the transmission mechanism, which may have its speed changing gears manually controlled, for eiiecting a circulation of oil in conjunction with the overdrive mechanism between the casings of the transmission and overdrive mechanisms.

Further objects of our invention are to provide an improved casing structure for the transmission and overdrive mechanism; and to protect the operating parts oi' the mechanism from damage due to foreign particles'which may nd their vway into the mechanism.

Still further objects of our invention reside in providing improvements in lubricating systems for power transmission mechanisms; in providing an improved lubricating system for planetary gearing especially of the type adapted for use in` automatic transmissions such as an overdrive gearing.

This application isa division of our copending application Serial No. 757,748, tiled Decem ber 17, 1934'. i

Further objects and advantages of our .invention will be more` apparent from the following illustrative embodiment of the principles of our,

invention, reference being had to the accompanying drawings in which:

Fig. 1 is a sectional elevational view through the` driving mechanism including the transmission and overdrive mechanism.

Fig. 2 is a partial top plan view of the driving mechanism with yparts of the casing structure broken away, the view being taken as indicated by the line 2--2 of Fig. l.

Fig. 3 is a side elevational view of a portion of the mechanism shown in Fig. 2.

Fig. 4 is a transverse' sectional elevational view taken as indicated by the line 4--4 of Fig. 2.

Fig. 5 is a detail sectional view of a portion of the manual control mechanism taken as indicated by the line 5-5 of Fig. 4.

Fig. 6 is a sectional view through a portion of the overrunning clutch taken vas indicated by line 6-6 of Fig. l.

Fig. is a sectional elevational view along line 1-1 of Fig. 1 showing the automatic clutch in its engaged position.

Fig. 8 is a sectional view oi the clutch illustrated in Fig. 7, the section being taken along line 8-8 of Fig. 7.

Fig. 9 is a detail sectional elevational view of only a portion of the mechanism illustrated in Fig. l showing the automatic clutch in the disengaged position, the manually controlled,cluteh being also-shown in another of its positions of control.

Fig. l is a View similar to Fig. 7 but showing the automatic clutch in its disengaged position, the view being taken along the line I U-I of Fig. 9.

Fig. 1l is a sectional elevational view along lineii--Ii of Fig. l, illustrating the overdrive oil circulating means.

Figs. 12 and 13 are detail views taken respectively along lines |2--l2 and I3-I3 of Fig. 11.

Fig. 14 is a detail sectional view along line |4--I4 of Fig. 13. A Fig. 15 is a further detail sectional view along the line I-I5 of Fig. 11.

In the drawings we have illustrated our driving mechanism A interposed between a speed ratio changing transmission B and the driven shaft i0, the latter extending rearwardly to drive the rear wheels (not shown) of the motor car or vehicle in the usual well-known manner, it

III

. of devices.

The transmission B may be of any suitable type such as the conventional selector type operated in the well-known manner through usual selector controls whereby the various adjustments may be made to the transmission in order to provide the speed ratios in the line of drive through -the transmission.

In order to realize certain advantages of our invention in a very simple manner, as will be more apparent hereinafter, we preferably provide a transmission B of the type having helical gears so that the helices, in addition to providing well-known advantages in the transmission art, provide further functions of pumping and circulating the lubricant in a novel manner in connection with the driving mechanism as a whole. Thus, as will be later described in greater detail. the helical gears are preferably so arranged that they pump lubricant for transmission B into the overdrive casing portion A without requiring an added pump.

The power coming from the usual engine' or other prime mover (not shown) which may be located forwardly of the transmission B drives the transmission from the engine drive shaft II and the power is taken from this transmission by a power driving means or shaft I4 having a forward piloting end rotatable in a bearing I5, the shaft having a reduced portion I9 extending rearwardly Vinto the portion of casing which contains the driving mechanism A. The drive shaft I4 slidably and loosely receives a collar 2U havingr an annular groove 2|. this collar having a rearward sleeve portion I6 terminating in a reduced splined hub portion I'I which slidably engages corresponding splines I formed exteriorly of the reduced shaft portion I9. The hub l'l provides a clutch shiftable along splines I8 by the collar 20 as will be presently apparent.

The parts of transmission B will be only briefly described as follows. The casing provides a bearing B for the shaft II. the latter having a rearward hollow portion receiving the aforesaid bearing i and the piloted forward and of shaft I4. The rear portion of shaft II is provided with a gear B2 in constant mesh with a gear B3 of the usual cuntershaft B4, the latter having second speed gear B5, low speed gear B11 and reverse gear B1. Journ'alled on shaft I4 is the second speed gear B8 in constant mesh with gear B5, a shiftable clutch B9 being selectively engageable with clutch teeth B1(J and E11 to provide direct and second speed drives from shaft II to shaft I4 as will be readily understood. The clutch B9 is illustrated as having the synchronizing member B12 of knowrA construction and operation. A shift lever B13 is manually rocked on pivot B11 in the usual manner to shift the rails B15, the latter having fingers B16 and B17 respectively engaging clutches B9 and the low speed and reverse4 .wardly of rollers 33.

matassa teeth, the teeth being inclined in relation to the direction of rotation of the gears to pump lubricant from the transmission reservoir B19 to the overdrive casing B20 as will be presently morel other things, an auxiliary driving means or mechanism between the driving and driven shafts I4 and I0 respectively, this driving means being preferably of a construction adapted to provide a speed ratio between these shafts of an overdriving character whereby driven' shaft I 0 may, under certain conditions hereinafter described, be driven from the driving shaft at a speed greater than a direct drive between these shafts, it being understood that the engine and driving shaft I4 will in such instances be relatively slowed down with respect to their normal speed of actuation for a given speed of vehicle travel. If desired, the mechanism A may be rearranged to provide an underdrive instead of an overdrive, although we prefer to arrange the gearing for an overdrive Aof v I the driven shaft Ill.

We preferably incorporate in our driving mechanism as a part of the primary driving means between driving shaft i4 and driven shaft Ill, an overrunning or free wheeling clutch D best shown in Figs. 1 and 6. This clutch may in itself be of any suitable form, the illustration showing a conventional device in which the inner cam member 28 is driven by internal teeth 29 engaged by the aforesaid teeth I 8 of the reduced portion I9 of shaft I4. A ring I8a prevents rearward displacement of cam 28. The inner cam member 28 has cam faces 32 engaged by cylinders 33 so that by the driving rotation of shaft I4, the high sides of cam faces 32 will wedge the cylinders 33 between cam member 28 and the outer cylindrical driven member 34 of the overrunning clutch to establish a direct drive thereto. The usual spacers 35 maintain the cylinders 33 in spaced position, and since the driven free wheeling part 34 is a forward extension of driven shaft I0 as shown in Fig. l, it will be apparent that whenever the engine or driving shaft I4 shows down, the vehicle and driven shaft I0 may, by reason of the clutch D overrun the driving shaft, other conditions permitting such action as will be presently apparent.,

A bearing 2li is provided between the inner and outer portions 28 and 34 of the clutch D for- Forwardly of bearing 23 the clutch portion 34 has an inner annular extension provided withl an annular series of internal clutch teeth or jaws 36 complementary to external teeth 30 of the shiftable clutch I7, the teeth 36 and 30 being adapted to interengage when the sleeve I6 is shifted rearwardly as will be presently apparent.

Referring now to the auxiliary driving gearing, we have illustrated this gearing as a planetary gearing although if desired other forms of gearing may be employed. In the illustrated embodiment and referring particularly to Fig. 1, the planetary gearing comprises a sun gear 3l fixed in a novel manner, hereinafter further described, to the transverse wall 40 between transmission B and the overdrive mechanism A, the shaft I9 and shiftable sleeve I6 freely rotating within this sun gear. A'planet carrier is provided with axially spaced rings 4I, 42 connected at circumferentially spaced intervals by the tie anastacia being maintained in spaced relationship by sleeves 44 respectively carried by the -tie members 43.* In Fig. 1, we have illustrated oneof these tie members 43 and associated sleeve 44.

Spaced circumferentially between the tie members 43 and the planet gear shafts 45 supported by the rings 4I, 42 and journalled by a bearing 46 on each of the shafts 45 are the planetary gear pinions 41` meshing with the aforesaid sun gear 31. 'Ihe planetary gears 41 also mesh with an internal gear 48 carried by a cylindrical sleeve 49 which projects forwardly from the outer member 34 of the free wheeling clutch D. The sleeve 49 may be formed as a part of the member I4 or may be rigidly connected thereto as by fasteners 50 shown in Fig. 1. The sleeve 49 has its axis concentric with the axis of shaft I4.

Our clutch C, best shown in. Figs. '1, 8 and 10,

preferably of the automatic type, has its cenwardly located plate or flange 55 receiving the rearwardly extending ends of the planetary gear shafts 45 whereby the shell 54 is driven by the planetary gears 41. Further details of the clutch C will be described hereinafter.

Theaforesaid annular groove 2| of collar 20 is engaged by a yoke 51, a portionof which is shown in Fig. 1, this yoke extending laterally through an arm 58 as seen in Fig. 2. The arm 58 is provided with a hollow hub 59 having a forward end slidably receiving the reduced portion 60 of the rod 6I, the latter having its forward end slidable in the casing bore 62. The rear end of hub 59 slidably receives an/ abutment 'sleeve 63 secured against rearward displacement along rod portion 60 by a screw 64 threaded in the rod.

Acting between sleeve 63 and the forward end of hub 59is a spring 65 reacting against the sleeve and urging hub 59 forwardly against the shoulder 65 of rod 6I. a

The rod 6I has slots 51 receiving the upwardly extending forks 68 of a'lever 68a rotatably journalled by a lateral .shaft 68b which projects outwardly through the casing to receive the lever 68c having its lower end connected to an actuating linkage such as a Bowden wire 68d. is slotted at 68e to receive a screw 68f to limit the swinging movement of the lever about its shaft 68h.

The lever 68u has a downwardly extending lever arm 68g (see Fig. 5) provided with a socket engaged by ball 68h. This ball is a part of plunger 68l slidably mounted in the upwardly opening cylinder 6 8J mounted for oscillation' on a shaft 6Bk (see Fig. 4). A spring 681 acts between plunger 68i and cylinder 681 and in the Fig. 5 position tends to hold the rod 6I in its forward position illustrated. When lever 69c is actuated to swing lever 68B toward the dotted line position, the angle between the plunger and cylinder is reversed and spring 681 then urges rod 6I rearwardly. Rod 6I is also held forwardly by a manually operable device in addition to the action of spring 681 as will be presently apparent.

Lever 689 v'Iiie aforesaid collar Il extends into the path of movement of the gear I2 when the latter is moved rearwardly for engagement-with the reverse idler gear Il as aforesaid. The arrangement is such that when the gear l! is shifted the reverse drive, provided that the mechanism is set to properly effect reverse as will be presently y apparent, collar llwill be ,engaged toward the latter part of the movement of gear I2 so as to into engagement with gear Il for establishing ly to engage teeth 35, 36 to lock out or render'the overrunning clutch D ineffective by providing a two-way drive between shafts I4 and I0'. During the aforesaid rearward shifting movement of hub 59, spring 65 will be compressed so that on release or forward movement of the gear I 2, the parts will be restored to the positions thereof illustrated in Fig. 2 provided, however, that other ycontrols for the shiftable parts are positioned to accommodate such return movement aswill be l presently apparent. When hub 89 moves rearwardly, as aforesaid, rod I is maintained against rearward movement by spring 681 acting in the position shown by the full lines in Fig. 5. 58 thus slides rearwardly on rod portion 60 and sleeve 53. y

In addition to the aforesaid manually operated means for shifting the position of clutch I1 in response to a setting of the reverse gearing of transmission B, we have also provideda further manually controlled means for shifting the clutch I1, at times when permitted by our improved controlling means, independently of the movement thereof under the influence of the reverse setting of the transmission. To thisl end, the

aforesaid Bowden wire 68d as diagrammatically` illustrated in Fig. 3, extends for convenient manipulation by the vehicle driver, such position being indicated by the usual dash. 69 which mounts a handle or knob 18 connected 'to the other end of the Bowden wire' 68d. 'I'he handle is adapted forl movement by the hand of the vehicle driver, this handle being guided from its position illustrated in Fig. 3 to a position in spaced relationship from dash 89, in which extended position the guide portion 1I of the handle registers a notch 12 thereof with spring pressed plunger 13 carried bya guide block 14.

The plunger 1l and'the notches 12 and 15 engageable therewith cooperate to advise the operator of the proper positioning of handle 10 for effecting the desired movement of the shiftable sleevel and clutch l'l. Furthermore, the plunger 13 when in the Fig. 3 position assists spring 681 in holding rod 8l fixed against rearward movement whenv clutch I1 is moved rearwardly by the reverse gear I2 as aforesaid. In Fig. 3 it will be noted that the plunger 13 is illustrated in engagement with the notch and inv this position spring 65 is acting to move the clutch I1 forwardly or to the position illustrated in Fig. l. In this `position the teeth of clutch I1 are free from engagement with the teeth 3S of the outer free wheeling clutch member 34.

It will be noted that when handle 10 is pulled outwardly from dash 69, lever arm 68 will move cylinder 681 and plunger 68lz to the dotted line position, spring 681 acts rearwardly on rod 6I as soon as the angle of the cylinder and plunger reverses, the spring 681 acting on rod 6I and hub 59 to shift sleeve I5 and clutch I1 to engage teeth 36 and 3l, this shifting movement of the Hub clutch ilunder control of the handle lll and under power of spring 581 being independent of a similar clutch shifting movement under the influence of reverse gear l2. When hub 59 is thus moved rearwardly the spring 55 is not fur.- ther compressed since hub 59 engages shoulder 55. Rod l, hub 59, spring 55 and sleeve 89 thus move as a unit. The manual control is thus made with very little effort required. In returning handle 19, the spring 891 snaps past its center line position and then acts to move rod 8| forwardly to restore clutch i1 to the Fig. 1 position, rod 5| acting through spring 55.*against hula 59. in holding clutch l1 in its positions of shift against undesired displacements. lt will be apparent that when gear l2 is shifted to engage the reverse gear i9, such movement is effective to shift the clutch l1 rearwardly into engagement with teeth 95 as aforesaid, hub 59 separatving from'its otherwise normally engaging position against shoulder 88. When the clutch l1 is shifted rearwardly by engagement of notch 12 with ball' 19, the clutch device will be maintained in theA aforesaid shifted position until the handle 19 is restored to the position illustrated in Fig. 3 whereupon spring 581 will act to restore the clutch to its position illustrated in Fig. 1.

Referring now to .the details of the clutch C which is preferably of the automatic type, one embodiment thereof being best illustrated in Figs. '7, 8 and 10, the pawl cage 52 is provided with diametrically arranged pairs of lateral extensions or pawl guides 16 and 11. Extensions 16 have pawl engaging faces 18 and extensions-11 have similar bearing faces 19. Fitting within shell 54 are a pair of the said pawls 5|, each having a face in sliding engagement with a face 18 of extension 16 and each-extending generally in-' .wardly of the pawl carrying cage.

Thus, each pawl is formed lwith a yoke portion 88 normally seated on an extension 11, each yoke portion having a guide counterbalancing portion 8| slidable intermediate a face 19 and the sides of the other pawl opposite the sides thereof in engagement with the face 18.

The face or side of each pawl 5| which slides against a face 18 has been designated by reference character 82 and this side of the pawl may be referred to as the coast side. The opposite side or face of each pawl 5| is indicated at 89 in sliding contact with the face 84 of the guide portion 8| of the other associated pawl. The drive side or face of each pawl 5| is indicated at 85 and it will be noted that this side 85 is offset from the side 83. Each pawl 5i has an outer cam face 86, it being noted that the drive side is spaced somewhat farther from the inner surface of shell 54 than the spacing of the other extremity of the coast side 82, when the clutch C is disengaged as shown in Fig. 10, so that the cam face 85 may be said to extendforwardly and radially inwardly of the direction of rotation of the clutch as indicated by the arrow 81 in Fig. 7. It will be noted that with the pawls 5| positioned as illustrated in Fig. 10, the cam face 8S at its highest point at the outer extremity of the coast side 82 has a small clearance with the inner surface of the slot carrying shell 54.

In order to normally urge the pawls 5| inwardly of the pawl cage 52 to position the parts as shown in Fig. l0, primary yielding means such as springs 89 are provided, each spring acting on the head 99 of a screw bolt 9| threadedly engaging suitable openings in extensions 11, the yoke Our mechanism is also of advantage' alavesa portions 89 being also provided with suitable openings so as to slidably receive the respective bolts 9| andv springs 89 cooperating therewith. Thus, the heads 90 of bolts 9| provide adjustable abutments for the compression of springs 89, these springs respectively acting at their operating ends on the yolre portions 89 of the pawls.

In order to provide a latching or locking action to 4correlate the manual operation of the shifting clutch |1 with the operation of clutch C, we preferably provideeach pawl 5i with a projection or finger 92, adjacenty the circular recessed portion 99 of the yoke portion 89 so that when clutch C is disengaged, as in Fig. 10, with the clutch il moved to lock out position of Fig. 9, the circular recess 99 of each pawl will fit around the main or large diameter part of sleeve I8 and thereby prevent the pawls 5i from moving outwardly. Sleeve i8 has an annular groove 94 at the forward reduced clutch forming end |1 thereof, this groove being bounded laxially by teeth 38 and a shoulder 95 so that when sleeve i6 is in the Fig. 1 position, the pawls may move outwardly to engage clutch C, the projections 92 being carried into groove 94. However, with clutch C so engaged, the sleeve i6 and clutch l1 cannot be shifted rearwardly because of shoulder 95 engaging the projections 92. Disengagement of clutch C moves projections 92 clear of groove 94, then permitting rearward shifting of clutch |1 by handle 18 or else by operation of the aforesaid reversing mechanism.

It will be noted that shifting of sleeve i6 is rendered very easy and without binding since our drive from shaft I4 to teeth 53 and 36 is not taken axially along sleeve i6 but merely through the forward end hub or clutching part |1 constituting a direct radial drive therethrough.

The shell 54 has the aforesaid plurality of circumferentially spaced pawl receiving slots or openings 55 suitably spaced so that diametrically arranged pairs of slots will simultaneously register with the pawls 5| to receive said pawls under conditions hereinafter more apparent.

The threaded ends of screw bolts 9| permit adjustment of the springs 89 when the heads 90 of these bolts are registered with one of the slots 55 of shell 54, it being understood that the sleeve 49 and outer casing may have one .or more aligned openings adapted for alignment with one of the slots 55 at the time of registration therewith of a bolt head 90 whereby adjustment of without the overdrive casing, the openings in the aforesaid sleeve being shown at 95a. The casing .opening 95b (see Fig. 1) is normally yclosed by a blug 95C.

When pawls 5| move outwardly into slots 55, such movement is limited by engagement of yoke portions 8|) with/'projections 16, the yoke portions sliding on bolts 9|.

Each pawl 5| is formed with a pocket 96 opening toward aface 94 of the associatedI counterbalancing guide portion 8| of the other pawl, each pocket 96 receiving secondary yielding means which may be in the form of a spring 91. Each spring 91 acts on a ball 98 movably housed within opening 95 adjacent the other end thereof. Each face 84 is provided with an inner ball receiving detent 99 and an outer ball receiving detent |99. Where it is desired to provide the outer detent |00 as well as the inner detent 99,

these cooperating pairs of detents are spacedV that when the pawls move outwardly together, the pawl 5| and associated guide 8| 4of the other pawl move in opposite directions and to the same extent. The purpose among other things of the detents 99 and |00 is to control the movement of the pawls so that they will quickly move outwardly and inwardly without hunting tendency.

In the operation of our improved driving mechanism, as thus far described, let it be presumed that the motor vehicle is being driven by the engine forwardly in direct drive with the clutch device Il in the Fig. 1 position but at a speed below that necessary for the centrifugal force to overcome the resistance of springs 89 and detents 98. Under suchconditions of normal drive, the drive shaft I4 provides a one-way direct drive to driven shaft I through the medium of the overrunning clutch D. During such drive the pawls 5| will be driven at the speed of drive shaft I4 and the slots 55 will be driven from the driven shaft I8 but at a slower speed by reason of the great train provided by the planetary gearing 48, 4l and 31.

The pawl springs 89 and detents 98 may be selected and adjusted for any desired speed of automatic engagement by clutch C for the overdrive and for purposes of illustration let it be presumed that this setting is such that the critical speed of engagement of clutch C takes place for approximately 45 miles per hour of vehicle travel. With the pawls driven from the engine, as illustrated, these pawls will be set so that they will be projected at a speed of the drive shaft such that when the engine is momentarily throttled down by a momentary release of the usual accelerator pedal, the speed of the slots 55 will remain approximately the same (assuming the vehicle does not perceptibly slow down during the overrunning action) and if such slot speed corresponded to 45 miles per hour or more of vehicle travel then when the pawls, on slowing down, synchronize in speed with the slots, the pawls will project into the slots to effect a smooth positive engagement of clutch C. As soon as engagement of clutch C takes place the drive from shaft i4 to shaft I8 is through the clutch C and planetary gearing to drive shaft I0 at a greater speed relative to driving shaft I4. At such time the overrunning clutch D is rendered automatically inoperative for any drive therethrough as soon as clutch C engages, the overrunning clutch portion 34 rotating faster than the inner cam portion 28 but in the same direction.

During the time that the drive shaft I4 is being slowed down as aforesaid to effect engagement of the clutch C at or above the critical speed thereof, the pawls go faster than the slots, the pawl cam faces 98 smoothly letting the pawls pass the slots. 'Ihe pawls will pass the slots until the speeds of the pawls and slots synchronize, at which time the pawls move outwardly to engage the pawl coast faces 82 in the coast sides of the slots. On speeding up the engine, the pawl drive faces 85 then drive the engaged drive sides of the slots for the overdrive condition, the outer detents |80 being then engaged by ball 98.

On deceleration of the vehicle below the critical speed of clutch C as determined by the outer detents |80, the pawls are retracted by springs 89 and the drive then is automatically restored to a, one-way drive through clutch D as before.

Whenever clutch device I1 is positioned as in Fig. l, the automatic overdrive may take place and when clutch C engages, the pawl projections 92 lock4 the sleeve I 6- against rearward shifting of the clutch I1 to lock-out position for cutch D.

At any time that clutch C is disengaged and the driver desires a direct two-way drive without free-wheeling, he may shift clutch I'I into engagement with teeth 36 whereupon the drive shaft will drive the driven shaft directly. In such position pawls 5| cannot move outwardly since the recesses 93 t around sleeve I6 as shown in Figs. 9 and 10. Furthermore, it will be noted that our clutch Il .is adapted for shifting without releasing the drive to the pawl cage whereby drifting of the pawl cage is avoided when driving in the lock-out position of clutch II. Thus, it is not necessary to synchronize the pawl cage and shiftable clutch I'I when returning to the one-way drive through clutch D, it being understood that when driving in the lock-out position of clutch I1 the pawls cannot y out even when the rotation of the pawl cage is above the critical speed owing to the pawl recesses 93 fitting around sleeve I6.

Thel clutch I1 may also be shifted to the lockout position by the manual reversing mechanism including the rearward slidable reverse gear I2 as aforesaid.

When in direct two-way drive, as when clutch II is in the Fig. 9 position, the clutch I'I is restored to the Fig. 1 position either by the hand operated member I0 or else by returning the reversing mechanism to a forward drive or to neutral.

If desired, the pawls 5| may be driven from the driven shaft and the slots driven from the driving shaft as will be readily apparent. The principles of such an arrangement are disclosed in the copending applications of Walter F. Ploetz Serial No. '707,052 and George L. McCain Serial No. '707,076 both led January 18, 1934. Other changes in the illustrated mechanism may also be made as desired without departing from the spirit Yand scope of our invention as dened by the appended claims.

We will now describe our improved lubricating and cooling system for the power driving mechanism.

While we have illustrated the coaxial shafts I I, I4 and I0 as extending horizontally in Fig. 1, it is generally desirable according to present common practice to slightly incline the engine rearwardly and downwardly and our power driving mechanism is intended to be likewise inclined when installed in the motor vehicle. Thus, when so installed the normally horizontal line |0| indicates the normal rearward and downward inclination of the entire power driving mechanism as will be readily understood.

The transmission reservoir B19 contains the lusual supply of lubricant and at the rear of the transmission casing the reverse gears l.'I and I3 have their teeth so inclined that they pump the lubricant continuously from the reservoir B19 rearwardly by throwing the lubricant from the periphery of the gears toward the aforesaid transverse partition Wall 40. In the path of the lubricant thus thrown toward wall 40, the latter has an opening |02 therethrough (see Fig. 11) whereby the lubricant is continuously supplied to the reservoir B2u of the overdrive mechanism A. A shelf or baile |03 is located near the bottom of opening |02 to assist in the transfer of the lubricant by catching and guiding some of the lubricant falling on the baille.

The lubricant thus introduced to the rear of wall 40 collects in the reservoir B20 and is pumped 7 5' or circulated therefrom through the overdrive mechanism. by the following illustrative means. The casing |04, of which reservoir B20 is a part. is cylindrical and has a series of lubricant guide baies |05, |06 and |01 spaced circumferentially thereof, these baliies being of varying height, viz. the dimension toward the rotary cylinder 49, to locate their inner edges closely adjacent the cylinder, the latter being eccentric with respect to casing |04 as shown in Fig. 11. The axis of cylinder 49 is preferably vertically above that of casing |04 toprovide a space at the bottom of the casing for the reservoir B20.

With cylinder 49 rotating counterclockwise as viewed in Fig.,l1, the cylinder 49 picks up the lubricant from reservoir B20 and a portion thereof is thrown against baie |05 which, as shown in Fig. 1, inclines forwardly and upwardly to guide the lubricant to an opening |08 in the wall 40. Thus, a portion of the lubricant is returned from reservoir B20 directly to reservoir B19 tending to maintain a uniform level of lubricant in these reservoirs and to also circulate the lubricant for cooling purposes as will be presently apparent.

A portion of the lubricant which escapes baflie |05 is carried by cylinder 49 and thrown off toward baffle |06, a remaining part which escapes baffle |06 being carried around by the cylinder for discharge against baiiie |01.

The baille |06 likewise slopes forwardly and upwardly to discharge lubricant guided thereby forwardly to a vertical passage |09 in wall 40, this passage being open only downwardly for lubricant discharge and rearwardly for lubricant entry.

The aforesaid sun gear 31 has a forward hub l l (see Fig. 12) adapted to journal the forward end of cylinder 49. Thus, hub I0 has a bearing member journalling the hub ||2 of the spider or support ||3 held for rotation with cylinder 49 between shoulder |4 and the abutment ring |5. The sun gear hub I0 has a forward and upward annulus ||6 terminating outwardly in the peripheral teeth ||1 which engage corresponding teeth 8 to form a central opening lin wall 40 through which shaft |4 and sleeve |6 project. The wall opening has a shoulder ||9 against which 'the annulus ||6 bears to limit forward movement of the sun gear 31, the latter being held xed by the engaged teeth I1 and |8.

Riveted to the front face of annulus ||6 ls a stamped annular plate |20 which, inwardly of passage |09 at the section shown in Fig. 12, has a forwardly deflected portion |2| cooperating with a radial passage |22 in annulus ||6 to form an inwardly extending passage for lubricant discharged from passage |09.

Secured by screw bolts |23 to the rear face of wall 40 is a stamped annular plate or shield |24 which is flat except at sections |2|2 and |5-|5. The inner edge of plate |24 is flared at |25 rearwardly and is spaced from hub ||2 to provide an annular lubricant passage |26 in continuous communication with passage |22. At section |2|2 opposite passage |09 plate |24 is flared rearwardly at |21 to provide a funnel-like lubricant entry between passages |09 and |2 so as to catch the lubricant from passage |09 and conduct the same downwardly for discharge rearwardly from passage |26 and form a further conduit or passage |28 at the lower end of annulus ||6. The plates |24 and |20 thus provide rear and front walls for the annulus passage |22.

The rotating spider ||3 has a plurality of @ross Reference land. successive registration with conduit spaced passages |29 therethrough for periodic |26 whereby lubricant is discharged therethrough to the axial passages |30 in the planetary shafts 45. The outer walls of spider passages |29 are flared rearwardly and outwardly at |3|, the forward ends thereof overlying the are |25 to efficiently conduct the lubricant and, by reason of the centrifugal force acting on the lubricant at passages |29, a. suction is created tending to forcibly withdraw the lubricant from annular passage |26.

Secured to the planet shafts 45 is a lubricant passage forming plate or ring |32 having a forwardly bent lower annular flange |33 adapted to overlap the rear edges of the flares |3| closely adjacent thereto as the spider passages |29 rotate relative to the rotating planet shafts 45. In order to secure plate |32 with shafts 45, the latter receive pins |34 which project outwardly into a ring |35, the plate |32 having its outer edge spun around a forward shoulder |36 of ring |35. The shaft passages 30 have a radial passage |31 for supplying lubricant to bearings 46 and rear outlets |38 for supplying lubricant to the movable parts of clutch C. The lubricant at bearings 46 and such lubricant as may pass between flange |33 and flares |3| will reach the planetary gearing for lubricating same.

Thus, in operation, the baffle |06 picks up and deects the lubricant thrown by centrifugal force from cylinder 49, conducting the lubricant through stationary conduits or passages |09, |22, |26 and |28. The lubricant discharged at |26 periodically enters the planet shaft passages |30 to lubricate the various parts of the planetary gearing and automatic clutch C while the lubricant discharged at |28 lubricates the bearing of spider ||3, working rearwardly to sun gear 31. The lubrication is by force, being under the pressure of the centrifugal action caused by rotation of cylinder 49.

Referring now to Figs. 1, 5, and 15, the baille |01 slopes forwardly and downwardly. In Fig. 1 this baiile is in front of the section but baille |01 is vshown in construction lines to indicate its slope.

Thus, balie |01 is sloped oppositely with respect to bailies and |06 since it is on the downward rotational side of cylinder 49 as viewed in Fig. 11, the slope of baiiie |01 also utilizing the force of gravity to conduct the lubricant forwardly to a system of passages shown in Fig. which is very similar in construction and purpose to the passages of Fig. 12. Corresponding parts are indicated wlth primed reference numerals and will only be briefly referred to since the operation and structure will be apparent from the foregoing description of the Fig. l2 parts.

Thus, baffle |01 supplies lubricant forwardly to passage |09', thence downwardly through annulus passage |22', plate |20 being flat since the passage 28 of Fig. l2 is omitted. Plate |24 is likewise flared at |21 and the top of the lflare has a notch |39 to accommodate rear movement of the rear end of rod 6| and sleeve 63 when displaced by knob 10 as aforesaid. The sleeve 63 thus slides in opening |40 to permit rod 6| to project across passage |09 and beyond notch |39 without interference. Lubricant ejected at |26 also periodically passes through spider passages |29 for the same purpose as in the Fig. 12 description.

With the view of supplementing the aforesaid supply of lubricant to passage |22' of the sun gear annulus |6, we have provided means for catching a portion of the lubricant thrown from the transmission gears and draining such lubricant under Examiner shown in Figs. 11, 13 and 14 wherein an upwardly opening trough i4| projects forwardly from an opening |42 in wall 40 above and to one side of gears B8, i2, and |3, these gears rotating to throw lubricant therefrom into trough |4I, the curved wall |43 thereof deilecting the lubricant into the trough'. This trough, when the transmission is tilted rearwardly as aforesaid, drains lubricant which flows rearwardly through opening |42 and downwardly through annulus passage |44 closed rearwardly by the bulged part |45 of plate- |24, passage |44 communicating with passage |22! by a passage |45.

The trough |4| is supported forwardly by an arm |41 thereof which is secured by fastener |48 between the transverse casing bridge |45 and the channel |50. The bridge .|48 is grooved to slidably accommodate the shifter rails B15, one groove being shown at |5| in Fig. 14. Bridge |48 andV channel |50 thus prevent vertical displacement of the shifter rails. A sheet metal cover |52 removably closes the top of the transmission. y Where the automatic clutch C is set to engage at relatively high vehicle travelling speed, such as referred to hereinbefore, it will be apparent that when the overdrive mechanism becomes active as a drive, the transmission B will ordinarily b e in direct driveso that there is no loading of the transmission gears. The heat generated in the overdrive mechanism A by reason of the operating gearing, bearings, and other working parts, is dissipated by the circulation of the lubricant to the transmission B, the latter acting as a Vcooling reservoir. When the transmission B is driving through a pair of its reduction gears, the over.

drive mechanism A is running light", viz. there is no vehicle power drive through the planetary gearing.

By reason of our invention, the alignment of the various shafts and rotatable assemblies is made more accurate, easier to manufacture and less costly. For example, one further feature of our invention resides in the provision of the support for the forward end'of the cylinder 49 in the wall 40, being centered therein by spider ||8 the sun gear annulus 5 independently of shaft I4,

the latter'having a two point bearing support at 5 and 25. These two points are easily and accurately lined up without any tendency to deflect the shaft at any intermediate point from any misaligned bearing. Furthermore, the shaft |4 being free of the sun gear 81 but co-axial therewith, provides a space for the shiftable sleeve l5, simplifying the control for the clutches Cand D. The

- casing for transmission B and overdrive mechaber 34 and cylinder 48 has a plurality of radial I passages |55 between screw bolts 50, these passages opening inwardly tothe radial passages or spaces |55 of an annular corrugated stamped plate |51. The plate passages |55 open inwardly just rearwardly of teeth 35 so that any chips or other foreign particles tending to accumulate at the teeth 30, 35, 53 and along shaft |4 will pass outwardly bycentrifugal force and with the ow of the circulating lubricant through passages |55 'and' |55 to accumulate harmlessly in the reservoir B20. The plate |51 -provides a rear wall for the passages |55 thereby protecting bearing 25 from foreign particles conducted outwardly through the forwardly extending hollow portion of the driven shaft. The inner edge of plate |51 is deflected aty |58 toward the side of camy 28 to 'further protect bearing 25 from foreign particles, these particles being guided by edge |58 outwardly into passages |55.

As will'be noted in Fig. 1, the baffles |05, |05 and |01 preferably terminate rearwardly short of the plane of passages |55 so that foreign particles discharged therefrom do not lodge on these bailies since otherwise they might be carried by the 1ubricant into circulating system for the overdrive mechanism.

As a further feature of our invention, it will be noted that according to the preferred embodiment of our'invention as illustrated, the casing structures for the transmission B and overdrive mechanism A including the transverse wall 40 are preferably integrally formed as by a unitary casing. This has the advantage of increasing the heat transfer between the casing structures thereby adding to the efficiency of the lubrication cooling system. The fiat walls of the transmission casing structure provide large cooling surfaces for efficiently cooling the oil heated by the transmis- 30 sion and overdrive mechanism,|the oil being contlnuously thrown to said walls by the transmisauxiliary driving mechanism operably connectedthereto, casing structures for each of said mechanisms, one of said casing structures providing a lubricant reservoir, means responsive to operation of said mechanisms for causing circulation of lubricant from said reservoir tol the other of said casing structures for lubricating the mechanism thereof and thence back to said. reservoir, a wall structure dividing said casing structures from each other and having a passageway for returning lubricant from the casing structure for said auxiliary mechanism to the casing structurev for said speed ratio changing mechanism, said auxiliary driving mechanism including a plurality of gears, means for supporting one of said gears from said wall structure, said auxiliary driving mechanism further including a rotary cylinder operably connected to' said gears, vand'means responslive to rotation of said cylinder for conducting lubricant picked up by and thrown from said cylinder into separate paths respectively directed through said wall passageway and to lubricate said gears.

2. In a motor vehicle power drive having a speed ratio changing mechanism and an auxiliary driving mechanism operably connected thereto, casing structures for each of said mechanisms, a wall between said casing structures, one cf said casing structures providing a lubricant reservoir, means responsive to operation of said mechanisms for causing circulation. of lubricant from said reservoir to the other of said casing structures for lubricating the mechanism thereof and thence back to said reservoir, said speed ratio changing mechanism including a rotary helical reverse driving gear disposed adjacent said wall and adapted to throw` `said lubricant toward the other of said casing structures, said wall having a lubricant conducting opening therethrough in the path of the lubricant thrown from said reverse gear, and auxiliary means for collecting lubricant thrown about in said first casing, in response to operation of said speed ratio mechanism, and conducting said collected lubricant by gravity to said second casing.

3. In a power ydriving mechanism, a casing structure adapted4 to receive lubricant, a driving shaft, a driven shaft, saicidriven .shaft having an enlarged end within said casing for receiving one end of said driving shaft, means including a gear train within said enlarged end of the driven shaft for driving said driven shaft from said driving shaft, said enlarged end having a passage extending generally radially therethrough, and a plate in said passage adapted to guide foreign particles outwardly therethrough.

4. In a power driving mechanism, a casing structure adapted to receivelubricant, a driving shaft, a driven shaft, said driven shaft having an enlarged end within said casing for receivirnig one end of said driving shaft, means including a gear train within said enlarged end of the driven shaft for driving said driven shaft from said driving shaft, said gear train including a planetary pinion engaging said enlarged end, a hollow shaft journalling said pinion, and a sun gear, an annular member adapted to secure said sun gear to a part of said casing, said casing part and annular member having radially aligned communicatinglubricant conducting passages, and means responsive to rotation of said enlarged end for conducting said lubricant to said communicating passages, and means for conducting said lubricant from said passages to said hollow shaft, said gear train further including a centrifugal clutch operable within said enlarged end adjacent said hollow shaft, said hollow shaft having an outlet passage adapted to supply lubricant therefrom to said clutch.

5. In a device of the character described, the combination with 'a' casing, of a rotating member in said casing and planetary pinions mounted on bearings requiringlubrication, lubricant conduits respectively extending into each of said bearings and parallel with` the axis of said member, a rotatable supportv for one end of said member extending adjacentione end of said bearings transversely of said bearing conduits, said support having a lubricant passage extending in the general direction of said axis, an annular plate overhanging the ends of said bearings, a stationarily mounted plate having a central opening and a flange adjacent said opening and entering one end of said lubricant passage during rotation of said support, said annular plate having a central opening and a ange adjacent thereto entering said lubricant passage at the other end thereof during rotation of said support, and means for conveying lubricant picked up by said rotating member within said casing on one side of said stationarily mounted plate to the other side thereof', the lubricant thus conveyed flowing through the opening in said stationarily mounted plate, through said lubricant passage and through the opening of said annular plate.

6. In a device of the character described, the combination with a casing, of planetary gearing in said casing including a rotating member and planetary pinions mounted on bearifgs requiring lubrication, conduits respectively extending through each of said bearings parallel with the axis of said member for conducting lubricant into said gearing, a rotatable support for one end of said member extending adjacent one end of said bearings transversely of said bearing conduits, said support having a lubricant passage extending in the general direction of said axis, an annular plate carried with said conduits and having a portionthereof overhanging the inlet ends of said conduits, a plate st-ationarily secured to a wall of said vcasing and having a portion thereof spaced apart therefrom, said stationary plate having a central opening therein and an annular ange surrounding said opening and projecting into said passage during rotation of said support, and means for conveying lubricant picked up by said rotating m'ember within said casing on one side of said stationary plate to theopposite side of said stationary plate and into the said space between said casing wall and said spaced portion of said stationary plate, the lubricant thus conveyed vflowing through the opening in said stationary plate, through said. Apassage and through the opening of said annular plate.

7. In a device of the character described, the combination with a casing, of a planetary gear mechanism comprising a member rotatably mounted in said casing and including pinions mounted on bearings, conduits extending through the axes of said bearings respectively, a rotatable plate mounted on said gear` mechanism Vand overhanging the entrance to said conduits, a fixed plate secured to said casing, said fixed plate having a central opening therein and an annular flange surrounding said opening, a rotatable support for one end of said member extending adjacent one end of said conduits, said support formed with a lubricant passage overhanging said to the opposite side of said fixed plate, the lubri` cant thus conveyed flowing through the opening in said fixed plate and thence through said passage and into said rotatable plate.

8. In a device of the character described, the combination with a casing, of aplanetary gearing having an internal ring gear rotatably mounted in said casing, said planetary gearing further including pinion gears meshed with said internal ring gear, hollow spindles for the pinion gears having radial openings therein, a pinion gear carrier, a ring secured on said pinion gear carrier and rotatable therewith and overhanging one of the ends-of each of said spindles, a shield stationarily mounted on said casing and having a central opening therein, a rotatable support for one end of the internal ring gear provided with a lubricant fpassage, said shield having a Iiange surrounding its said opening and projecting into said passage during rotation of said support, and means for conveying lubricant picked up by a rotating member of said planetary gearing on one side of said shield to the opposite side of said shield, the lubricant thus conveyed iiowing through said shield opening and support passage and into said ring.

9. In a device of the-character described, the combination with a. casing, of a planetary gearing including a rotary internal gear member v v2,127,354. and planetary pinions mounted on bearings requiring lubrication, a support for one end of said rotary member adjacent said pinions, lubricant conduits respectively extending` into each of said bearings and parallel with the axis of said'member, an annular ring overhanging one of the ends of each of said bearings and rotatable therewith on one side of said support. a stationary shield adjacent the other side of said support, said shield having a portion thereof spaced from a wall of said casing to provide a lubricant passageway, means for conveying lubricant picked up by said rotary member within said casing on one side of saidshield to the opposite side of said shield and into said passageway, and means for conducting lubricant from said passageway through said shield and support and into said annular ring for passage ofthe lubricant into said bearing conduits. i

10. In a device of the character described, the combination with a casing. of a planetary gearlng mounted in said casing including a ring gear. a stationarily mounted sun gear, pinion gears nested between said ring and sun gears, pinion shafts for said pinion gears, lubricant conduits extending through said shafts to the interior of said gearing, an annular ring mounted to rotate with said pinion shafts and overhanging one end of each of said conduits, a shield ilxed to said casing and having an opening extending from one side of said shield to the other toward said shaft conduits. a support for one end of said ring gear disposed between said annular ring and shield and having an opening therethrough, and means for delivering lubricant to that side of said shield opposite from said support, said lubricant flowing through said shield and support opening and into said ring, and from thence through said shaft conduits to the interior of said planetary gearing.

ll.4 In a device of the character described, the

combination with a pair of lubricant-receivingcasings having a transverse wall therebetween, of change speed gearing in one of said casingsy and supplemental gearing in the other, said supplemental gearing including a rotary member and a plurality of operating partsl requiringlubrication, said transverse wall having a pair of lubricant conducting"y openings therethrough, means responsive to operation of said change speed gearing for picking up lubricant from within the casing thereof and directing the same through one of said openings to the other of said casings, means for conveying lubricant picked up by said rotary member from within the casing of said supplemental gearing to said operating parts. and means responsive to rotation of said rotary member for conducting lubricant picked up bysaid rotary member and thrown therefrom forcibly I.

said'wall openings to lthe through the -other of casing of said change speed gearing.

' 12. In a device oi' the character described, the combination with a `pair of lubricant-receiving casings having a transverse wall therebetween, of change speed gearing in one of saidcasings and supplemental gearing in the other, said supv plemental gearing including a rotary member v and a plurality of operating parts requiring lubrication. said transverse wall having .a pair' of lubricant conducting openings therethrough, means responsive to operationv of said change 'esileeciggaf*ing for picking 'up lubricant from within the casingthereof anddirecting the same" i through one of said openings to the "other of l said Il casings, and means for conveying lubricant picked up by and thrown from said :rotary member in separate paths respectively to said operating parts and through the other of said wall openings back to said change speed gearing casing.

Y 13. In a device of the character described having a pair of adjoining lubricant-receiving casings and a wall therebetween, said wail having a pair or lubricant conductingopenings therethrough, changev speed gearing in one of said casings,-planetary gearing in the other of said casings including a rotatable member and a plurality of planetary pinion bearings requiring lubrication, means responsive to operation of said change speed gearing for .directing lubricant from the casing thereof through one of said wall openings to the other of said casings for contact with said rotatable member. and means for conducting and directing lubricant picked-up by and thrown from said rotatable .member in separate paths respectively to said bearings and through the other ot said wall openings back to said speed ratio changing casing. t

14. In a device of the character described having a pair of adjoining lubricant-receiving casings and a wall therebetween, said wall having a pair of lubricant conducting openings therethrough, change speed gearing in one of said casings, planetary gearing in the other oi' said casings including a rotatable member, a plurality of planetary pinion bearings lubrication and a support for one end of v rotatable member between said wall and on bearings, means responsive to operation of said change speed gearing for directing lubricant from the thereof through one of said wall openings to the other of said casings for contact with said rotatable member, means lor conveying lubricant pickedI jup by and thrown from said rotatable member in separate paths respectively from one side of said support to the other side and through the other of said wall ol` nings back to said speed ratio changing casing, means for conducting Y lubricant from the `lst said side of said support to the other side thereof within said rotatable 4member andto said pinion bearings.

l5. In a power driving mechanism. a tranamission gearing and housing therefor having a lubricant reservoir, a casing adjacent said housing and adapted to receive lubricant, a wall transversely separating said housing and casing and having a lubricant passageway therethrough for placing said casing in communication with said housing,` `a. driving shaft, a driven shaft, means within said casing including a gear train forl driving said driven shaft from said driving shaft.

.said casing having a pair of lubricant defiecting balles projecting inwardly therefrom. one of said. bailies being disposed adjacent' said wail passageway for directing lubricant thereto for passage of the lubricant from said casing to said housing. a rotary element oper-ably connected to said gear train anddisposedadiacentsaidbaiileswherebylubricant thrown from said rotary element is ycaught by said bailes and directed therealong in separate streams, and lubricant conducting means within am ming :or ammonimencant from the'othe'r ofv said to said gear,

'iarnsdevlortheennt'ardmnbeams combination with a casing structure, of a planetary gearingwithln'sald and including a rotary internal member and planetary pinions mounted on bearings requiring lubrication, said gearstructure chorod-tosaid easing structure,

said stnictures beimv provided with gearingfurtherincludingasini'y n cluding a rotary internal gear member and i planetary pinions mounted on bearings requiring lubrication, said gearing further including a sun gear structure anchoredlto said casing structure, a plate ixed adjacent said structures' and cooperating therewith to provide a lubricant passage` for supplying lubricant to said pinion bearings, means for introducing lubricant to said plateforming passage, and means disposed between said plate-forming passage and said pinion bearings for supporting one end of said internal gear member on said sun gear structure, said supporting means `having an opening accommodating passage of lubricant from said plateforming passage to said pinion bearings.

18. In a device of the character described, the

.combination with a casing structure, of a planetary gearing within said casing structure and including a rotary internal gear member and planetary pinions mounted on bearings requiring lubrication, said gearing further including a sun gear structure anchored to` s aid casing structure. said structures being provided with communieating lubricant passages for supplying lubricant to said pinion bearings, means supporting one end of said internal gear member on said sun gear structure, said supporting means having an opening accommodating passage of lubricant from 'one side thereof to the other to pass lubricant from said communicating passages to said pinion bearings, means for introducing lubricant to one-of said communicating passages, and an annular ring overhanging one of the ends of each of said pinion bearings for guiding lubricant yfrom 'the opening of said supporting means toward said pinion bearings.

19. In a device of the character described, the combination with a casing structure, of a planetary gearing within said casing structure and including a rotary internal gear member and planetary pinions mounted on vbearings requiring lubrication, said gearing further including a sun gear structure anchoredfto said casing structure, said structures being provided with communicating lubricant passages for supplying lubricant to said pinion bearings, means supporting one end of said internal gear member on said sun gear structure, said supporting means having an opening accommodating passage of lubricant from one side thereof to the other to pass lubricant from said communicating passages to said pinion bearings, means for introducing lubricant `therethrough adapted to successsively side of said ananas@ to one of said communicating passages, and an annular ring overhanging one of the ends of each oi said pinion bearings for guiding lubricant from the opening of said supporting means toward said pinion bearings, said annular ring having a marginal portion thereof deflected into said opening.

20. In a device of the character described, the combination with a casing structure, of a planetary gearing within said casing structure and including a rotary internal gear member and planetary pinions mounted on bearings requiring lubrication, said gearing further including a sun gear structure anchored to said casing structure, said structures being provided with communicating lubricant passages for supplying lubricant to said pinion bearings, means supporting one end of said internal gear member on said sun gear structure, said supporting means having an opening accommodating passage of lubricant from one side thereof to the other to pass lubricant from said communicating passages to said pinion bearings, means for introducing lubricant to one of said communicating passages, an annular ring overhanging one of the ends of each of said vpinion bearings for guiding lubricant from the opening of said supporting means toward said pinion bearings, ture drivingly connected to said planetary gearing disposed adjacent the other ends of said pinion bearings for receiving lubricant therefrom.

21. In a device of the character described. the combination with a casing structure. of a planetary gearing within said casing structure and including a rotary internal gear member and planetary pinions mounted on bearings requiring lubrication, said gearing further including a sun gear structure anchored to said casing strucand a clutching structure, said structures being provided with communicating lubricant passages for supplying lubricant to said pinion bearings, a rotatable support for one end of said internal gear member, said support having a plurality of openings register with said communicating passages for passing lubricant therefrom through said rotatable support of said pinion bearings, and means for introducing lubricant to one of said communieating passages.

22. In a device oi' the character described, the combination with a casing strucure, of a planetary gearing within said casing structure and including a. rotary internal gear member and planetary pinions mounted on bearings requiring lubrication. support means for one end of said internal gear member, means for supplying lubricant to gne side of said support means, and means for conducting lubricant from said supply support to the other side thereof for lubricating said pinion bearings.

o'rro 'n FrsHBURN. HERBERT r'. PATTERSON.' RICHARD c. ALAND. 

